US20070158891A1 - Quick action clamping cylinder with a simplified structure - Google Patents

Quick action clamping cylinder with a simplified structure Download PDF

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Publication number
US20070158891A1
US20070158891A1 US10/553,712 US55371204A US2007158891A1 US 20070158891 A1 US20070158891 A1 US 20070158891A1 US 55371204 A US55371204 A US 55371204A US 2007158891 A1 US2007158891 A1 US 2007158891A1
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Prior art keywords
quick
action clamping
clamping cylinder
piston
cover
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Abandoned
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US10/553,712
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English (en)
Inventor
Emil Stark
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Ssa System Spann AG
Andreas Maier GmbH and Co KG
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Ssa System Spann AG
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Assigned to SSA SYSTEM-SPANN AG reassignment SSA SYSTEM-SPANN AG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: STARK, EMIL
Publication of US20070158891A1 publication Critical patent/US20070158891A1/en
Assigned to ANDREAS MAIER GMBH & CO. KG reassignment ANDREAS MAIER GMBH & CO. KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SSA SYSTEM-SPANN AG
Abandoned legal-status Critical Current

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
    • B23Q11/00—Accessories fitted to machine tools for keeping tools or parts of the machine in good working condition or for cooling work; Safety devices specially combined with or arranged in, or specially adapted for use in connection with, machine tools
    • B23Q11/08—Protective coverings for parts of machine tools; Splash guards
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
    • B23Q1/00—Members which are comprised in the general build-up of a form of machine, particularly relatively large fixed members
    • B23Q1/0063—Connecting non-slidable parts of machine tools to each other
    • B23Q1/0072—Connecting non-slidable parts of machine tools to each other using a clamping opening for receiving an insertion bolt or nipple

Definitions

  • the invention relates to a quick-action clamping cylinder with a simplified structure according to preamble claim 1 .
  • a quick-action clamping cylinder of the aforedescribed type is disclosed, for example, in DE 101 18 808 A1 of the same applicant.
  • this disclosed quick-action clamping cylinder does not have a simplified structure, because the ball are locked by two pistons moving against each other.
  • a spring assembly operates on one piston, whereas the other (smaller piston) is driven by a dedicated compression spring and displaced in the cylinder space of the larger piston.
  • this conventional design has a large number of moving parts, so that assembly and maintenance of this type of quick-action cylinder is quite complex.
  • the force of the coil spring assembly or disk spring assembly is converted to a retraction force acting on the retractable nipple only with a ratio of 1:1.
  • the disk spring operates directly on the larger force-producing piston, and the smaller piston follows the movement of the larger force piston and moves the ball inward toward the radially inwardly supported retractable nipple with the force produced by the small spring.
  • the conventional arrangement has the additional disadvantage that an upper pressure space formed for the pressure oil has a large retention volume and is formed on the bottom side of the cover. A large quantity of pressure oil is required due to the large retention volume. The location of the upper pressure space below the cover may also cause the pressure space to bulge the cover upwardly, which results in an inaccurate position of the workpiece palette resting on the cover.
  • the number of possible load change cycles is limited due to the large fill volume of pressure space, because of the oil must be completely removed from the cylinder space before a new load change.
  • the small contact surfaces of the small-sized locking balls on the associated contact surfaces on the retractable nipple produce indentations on the contact surfaces on the retractable nipple after longer operating times of the clamping system, which can change the retraction force.
  • the undesirable indentations caused by the locking balls on the outside periphery of the retractable nipple can even remove material in the form of chips, which can adhere to the retractable nipple and can prevent the retractable nipple from being pulled out of the central opening in the clamping cylinder.
  • the piston and the retractable nipple of the conventional clamping cylinder were fabricated entirely from a high-hardness tool steel, which tends to be a rather brittle material and is expensive to manufacture.
  • the object of the invention is solved by the technical teachings of claim 1 .
  • the clamping system consists essentially of a piston which is displaceably and sealingly guided between the surfaces of the cover and the housing.
  • the piston has radially inner, slightly sloped chamfers, with which the locking balls make contact in a load-transmitting fashion.
  • the locking balls contact the bottom side of the cover, and contact in a third ball position an oppositely sloped chamfer disposed on the outer periphery of the retractable nipple.
  • the piston is pre-biased in its locked position in a conventional manner by a spring assembly.
  • the spring assembly can include disk springs, coil springs or other resilient force reservoirs.
  • a corresponding counterpressure can also be produced by a fluid or a gas, instead of by a spring assembly.
  • the balls now contact two chamfers oriented in opposites directions, i.e., on one hand, a chamfer disposed on the piston, which urges the ball against the bottom side of the cover and, on the other hand, an opposing chamfer of the outer periphery of the retractable nipple, which is sloped opposite to the aforementioned chamfer on the cylinder.
  • the first-mentioned sloped surface on the piston has, for example, an angle of 3° to 6°, preferably 5°, so that the slope is relatively small and is in the self-locking range, because it is below the self- locking limit of 7°.
  • the force of the spring assembly is in effect transferred to the retractable nipple as a corresponding retraction force with a ratio of, for example, 1:6.
  • the locking balls act as a lever arm and convert the force of the disk springs into a larger retraction force on the retractable nipple.
  • the locking balls can now have a large size, because the housing provides more interior space, and because the balls are unconstrained and no longer require a cage.
  • the balls are no longer exposed to shear forces, but only to compression forces.
  • the balls assume a stable three-point support, because the radially outer section of each ball contacts the inside of the piston, whereas the vertically upper section contacts the bottom side of the cover and the radially inner section contacts the outer surface of the retractable nipple.
  • This stable position defined by three ball positions produces a uniform force of the balls, so that the balls they need no longer be made of an expensive material, because significantly smaller ball pressure forces are produced.
  • the balls can be manufactured from a relatively low-quality case-hardened steel. Only the outer periphery of the balls needs to be hardened, whereas the inner core can be made of a relatively soft metallic material.
  • the balls themselves are then advantageously elastically deformable to a certain extent and can also elastically deform because of the three-point support. If the retraction forces are asymmetric or the load is distributed asymmetrically over the workpiece palette, then the elastic deformation of the various locking balls can compensate canting forces in certain peripheral regions on the retractable nipple, because the elastic deformation causes the balls to orient themselves uniformly and become centered on the outer periphery of the retractable nipple.
  • Manufacturing tolerances of the clamping system are also compensated by the partial elastic deformability of the balls, which are automatically centered in the region of the three-point support on the retractable nipple.
  • lever transmission ratio provides a mechanical advantage of 1:6.5, retraction forces in a range of 20,000 N can be achieved with a significantly smaller housing for the quick-action clamping cylinder and smaller disk springs. Conventionally, retraction forces of only approximately 6,722 N are achievable with larger disk springs and larger housing diameters.
  • the invention is also based on the observation that the balls can also be used to provide automatically centering on the retractable nipple, because corresponding material deformations are explicitly permitted.
  • the retractable nipple is completely positively locked due to the three-point support of the locking balls.
  • the aforementioned, relatively small slope of the chamfer on the piston results in self-locking of the locking balls in the locked state.
  • the locked retractable nipple can then no longer be pulled upwardly out of the quick-action clamping cylinder against the applied retraction force.
  • the retractable nipple can still be pulled out of the housing of the quick-action clamping cylinder against the applied spring force by a small displacement of, for example, 2 mm, even if the retractable nipple is locked. This is possible because the locking balls are supported in a ball cage which, when the locking force is exceeded, makes contact with an associated surface on the housing only after being displaced over a certain distance.
  • the balls are in a self-locked state due to the small-slope chamfer on the piston. Even if one spring of several disk springs uniformly arranged along the periphery breaks, the locked state can still be maintained. The locked state is maintained, because each ball is in self-locking engagement.
  • the clamping system of the invention has a surprisingly small number of parts.
  • the number of parts is further reduced by combining several parts to a so-called built-in module.
  • the spring assembly is combined with the lower section of the clamping system and the ball support to a so-called built-in module.
  • the clamping system can then also be installed in an overhead location or vertically, which is impossible with conventional systems.
  • the disk springs had to be inserted very precisely in the interior space of the housing with the cover removed, before the cover could be closed. Accordingly, a vertical or overhead installation is then not possible, because the disk springs cannot be uniformly positioned along the periphery in the housing and accurately attached, due to their tendency to move around before the cover can be screwed on.
  • the built-in modules can be preassembled, which simplifies installation and allows a faster exchange.
  • Such locking inquiry is not necessary with the invention. For example, if the pressure oil for operating the piston is missing and if the piston is in the locked position, where the balls are moved radially inwardly into the center opening of the clamping system, then according to the invention, the retractable nipple cannot be moved into the center opening of the clamping system.
  • the retractable nipple makes contact with the outside periphery of the radially inner large-volume locking balls, but is unable to move past the locking balls, so that an apparent locked position cannot be attained.
  • the large insertion depth of the locking balls projecting into the center opening of the housing prevents the retractable nipple from moving into the locked position, so that the retractable nipple cannot move farther into the housing.
  • FIG. 1 a cross-sectional view of a first embodiment of a quick-action clamping cylinder according to the invention
  • FIG. 2 a detail of the arrangement of FIG. 1 ;
  • FIG. 3 a cross-sectional view of a second embodiment of a quick-action clamping cylinder with blow-out air;
  • FIG. 4 a cross-sectional view of another embodiment of a quick-action clamping cylinder with an unobstructed center bore, which can be used as fluid drain or inlet for blow-out air;
  • FIG. 5 a cross-sectional view through the first embodiment of a built-in module
  • FIG. 6 a cross-sectional view through a second embodiment of a built-in module
  • FIG. 7 a cross-sectional through a built-in module of a quick-action clamping cylinder, which can be inserted into an associated opening in a machine table or a clamping plate;
  • FIG. 8 a top view of the arrangement of FIG. 7 with the workpiece palette removed;
  • FIG. 9 the same diagram of a quick-action clamping cylinder as illustrated in FIG. 3 , with an added workpiece pallet;
  • FIG. 10 a top view of the arrangement of FIG. 9 and FIG. 3 , with the workpiece palette removed;
  • FIG. 11 a cross-sectional through another embodiment of a quick-action clamping cylinder in form of a built-in cartridge
  • FIG. 12 a cross-sectional through another embodiment of a quick-action clamping cylinder with a central ejector
  • FIG. 13 a cross-section through another embodiment of a quick-action clamping cylinder in the form of a built-in cartridge with two different pressure connections;
  • FIG. 14 a modified embodiment of FIG. 13 as a surface-mounted cylinder.
  • FIG. 1 shows a general schematic diagram of a quick-action clamping cylinder, which preferably includes a tubular housing 1 , which is mounted on a machine table or a clamping plate (not shown) with screws 15 and an associated tensioning ring 16 .
  • the tensioning ring 16 is connected to the tubular housing 1 by a safety ring protruding into both parts.
  • the quick-action clamping cylinder has an upper cover 2 with supports screws 19 which are uniformly distributed along the periphery and used to secure the cover 2 on the top side of the tubular housing 1 .
  • the upper safety ring 18 on the cover 2 serves as a stop for a corresponding sheet metal cover for covering the top side of the quick-action clamping cylinder.
  • the retractable nipple 3 is inserted into the center opening 32 of the quick-action clamping cylinder from above, as shown in two different clamping positions. In the right-hand partial cross-section, the retractable nipple 3 ′ is shown in the locked position, whereas the left-hand partial cross-section shows the unlocked state of the locking system.
  • the locking system is essentially formed by a piston 4 , which according to FIG. 2 is formed as an offset tubular part with an upper unsupported ring-shaped projection 104 , which transitions via an offset into another radially outer ring-shaped projection 106 , which is sealingly guided on corresponding interior surfaces of the tubular housing 1 .
  • the outside of the piston 4 sealingly contacts via corresponding sealing rings a corresponding cover projection 105 , which is also unsupported and is thick enough to prevent bending.
  • the ring-shaped projection 104 of the piston 4 can be partially deformed in the radially outward direction.
  • the locking balls 21 which are uniformly distributed along the periphery, are supported on the bottom on corresponding radial ball raceways 92 of a ball support 5 .
  • the ball support forms in the radially inward direction a corresponding circumferential, approximately lobe-shaped, upwardly oriented ball support 34 for securing the position of the locking balls 21 .
  • the locking balls are also held captive on the cover inside of the cover 2 by corresponding ball mounts 27 , whereby both the ball mounts 27 and the ball mounts 34 do not transfer loads.
  • the ball support 5 is connected via a thread 60 with a lower spring support 6 , with both parts forming a built-in module.
  • the two parts form a circulatory receiving space for the springs 7 which are uniformly distributed along the periphery.
  • each spring 7 contacts in the radial outward direction a corresponding radially outer upper spring support surface 35 on the bottom side of the piston 4 and also rests on a radially outter lower spring support surface 36 of the spring support 6 .
  • the radially outer spring support surfaces 35 , 36 prevent undesirable bending of the bottom of the spring support 6 .
  • the radially outer upper spring support surface 35 is advantageously in approximate alignment below the cylinder space 12 , so that the cylinder space 12 is not deformed when the locked position is released.
  • the lower spring support is fitted in the tubular housing 1 by locking balls 6 uniformly distributed along the periphery. According to FIG. 2 , the locking balls 8 contact the sloped chamfers 37 on the spring support 6 , with corresponding grooves guiding the locking balls 8 arranged in the region of the chamfer 37 .
  • the grooves 38 are uniformly distributed along the periphery and match the number of the employed locking balls 8 to prevent the locking balls from moving in the circumferential direction.
  • the locking balls 8 contact a lower radius 40 in the region of the tubular housing 1 and also a radius 31 oriented in the opposite direction in the region of the tubular housing 1 .
  • the chamfer 37 thereby urges the locking balls 8 into the two opposing radii 39 , 40 , providing an absolutely secure connection for transferring large loads between the inner built-in module of the locking system and the tubular housing.
  • a radially outer circumferential recess 9 is provided for guiding the blow-off air. This type of air feed will be described below.
  • a cylindrical threaded section 10 which can be connected with a cover and will be further described below, is formed on the bottom side of the spring support 6 .
  • a pressure medium is introduced into the interior space of the tubular housing 1 via a pressure connection 11 , whereby any suitable material in conformance with the general description may be selected as the pressure medium.
  • any suitable material in conformance with the general description may be selected as the pressure medium.
  • the following description refers to a pressure oil or hydraulic oil, although the invention is not limited thereto.
  • the pressure oil is introduced via the pressure connection 11 into a corresponding blind hole 13 , which is in fluid connection via a ring-shaped recess 14 with the cylinder space 12 .
  • the pressure oil is supplied to the piston 4 via this cylinder space.
  • a very small-volume cylinder space 12 is produced, on one hand, by the cover projection 105 of the cover 2 and, on the other hand, by the offset in the piston 4 , so that only very small fill quantities are required. Because the small volume of the cylinder space 12 , loads can be changed rapidly without unintentional disadvantageous deformation of the cover by the supplied oil, because pressure space has an increased cross-sectional thickness in the region of the cover projection 105 .
  • the cylinder space 12 is then also arranged farther outward in the tubular housing 1 , namely proximate to the radially outer screws 19 between the cover 2 and tubular housing 1 . Deformation forces applied to the cover are then advantageously absorbed by the screws 19 .
  • the transition region in the cover between the downwardly extended cover projection 105 and the material of the cover, through which the screws 19 extend, can thereby be made strong and is capable of transferring large loads without deformation.
  • the cover needs to be thicker only in the radially outer region (beyond the locking balls 21 and the piston 4 ), the cover can have a reduced thickness in the inner region, so that the locking system installed in this region can have a smaller size.
  • the thickness decreases to only approximately 7 mm in the region of the locking balls 21 .
  • This region of the locking system can hence be equipped with large locking balls capable of transferring large loads.
  • the overall installation height of the entire quick-action clamping system can then be significantly reduced compared to conventional systems.
  • each locking ball 21 makes contact in a radially outer position 24 with a corresponding slightly sloped chamfer 25 on the inner periphery of the piston 4 .
  • the slightly sloped chamfer 26 continuous in the axial direction to a chamfer 26 with a greater slope.
  • the chamfer 26 with the greater slope is used to apply a so-called rapid lift.
  • each locking ball should be moved as quickly as possible outwardly across the chamfer 26 with the greater slope into the unlocked position.
  • the locking ball 21 is then quickly moved out of the region of the (force) chamfer 25 by a corresponding released stroke, so that the locking ball 21 immediately reaches the chamfer 26 with the greater slope and disengages from the retractable nipple 3 .
  • the mechanical advantage of the lever is achieved by urging the springs 7 initially against the bottom side of the piston 4 in the region of the spring support surface 35 .
  • This pressing force is transferred via the tubular ring-shaped projection 104 of the piston to the chamfer 25 with the smaller slope, where the balls make contact in a corresponding position 24 .
  • the spring force is now transferred at the position 24 via the level arm 102 to the upper ball support point on the bottom side of the cover 2 at position 22 , where each locking ball is supported, forming another level arm 103 , which terminates on the inner periphery of the retractable nipple 3 with the ball supported at position 23 .
  • Each locking sphere 21 forms a lever 29 resulting from the combination of the two level arms 102 and 103 .
  • This makes it possible for the first time to transfer the spring force of the springs 7 at position 24 with a ratio of, for example, 1:6.5 to the corresponding position 23 on the outer periphery of the retractable nipple 3 .
  • the retractable nipple 3 is then pulled into the central interior space 32 of the housing of the clamping system by a retraction force which is enhanced by a factor of 6.5.
  • the chamfer 28 of the retractable nipple 3 has a greater slope than the chamfer 25 on the piston 4 .
  • the large slope of the chamfer 28 generates a very large and stable retraction force, so that each locking ball enters the associated unlocked position 33 of the retractable nipple 3 with a large insertion depth.
  • Conventional locking balls have a diameter of 5 mm, which results a usable surface of approximately 78.54 mm 2 .
  • balls with a diameter of, for example, 14 mm can be used which results in a usable ball surface of 615.75 mm 2 . Accordingly, the surface is increased by 784%, which is one reason for the aforedescribed advantages.
  • the locking balls 21 In addition to the elastically deformable ball surface, the locking balls 21 also have a very large insertion depth into the central unlocked position 33 on the retractable nipple 3 . This prevents material shearing or material removal in the region of the chamfer 28 , because the chamfer 28 , unlike in conventional systems, has a relatively large angle with respect to the vertical direction.
  • the workpiece pallet connected with the retractable nipple 3 may inadvertently be pulled out in the locked position against the retraction force, which can cause severe damage to the material in the region of the chamfer 28 .
  • This is prevented by the invention, because the balls that contact the chamfer 28 have a large surface and a large retraction force, preventing damage to the chamfer 28 .
  • the conical tip of the retractable nipple 3 engages with the center interior space 30 in the clamping cylinder, whereby the space can also be open to the bottom, as will be described below.
  • the direction of the arrow 31 on the lever 29 in FIG. 1 also shows that the lever 29 tilts, i.e., that the lever force is transferred in the direction of the arrow 31 from the piston 4 to the outer periphery of the retractable nipple 3 .
  • the interior space 30 can also provided with blow-off air.
  • a vertically oriented bore 48 which is open on one side and whose function will be described below, is arranged in the spring support 6 .
  • the ring-shaped recess 20 is disposed on the topside of the spring support 6 to deflect the air.
  • FIG. 3 shows an embodiment which is slightly modified from FIG. 1 , and includes novel air pathways for blow-off air.
  • a corresponding gas, compressed air or a coolant are introduced into the tubular housing 1 through the air connection 44 , from where the reach through an ascending vertical bore the lower region of the tubular housing 1 , where the pressure medium enters the annular recess 9 .
  • a cover 42 is screwed onto the thread 10 , producing a gap 43 between the bottom side of the spring support 6 and the inside of the cover 42 for guiding the pressure medium.
  • the pressure medium flows, in one hand, via a recess 9 arranged on the outside periphery and, on the other hand, into the center region, where it enters via the gap 43 associated vertically ascending bores 45 . From there, the compressed air moves via the aforementioned circular groove 20 and from there again via upwardly sloped grooves 46 , which terminate in the ball raceways 92 . In this way, the ball raceways 92 are cleaned by the blow-off air.
  • the sloped bore 46 has not only an angle relative to the vertical in the drawing plane of FIG. 3 , but also perpendicular to the drawing plane of FIG. 3 .
  • an air current which impinges the bottom side of the locking balls 21 at an angle is directed to the ball raceways 92 and rotatably drives the locking balls in the direction of arrow 74 , which then circulate on the ball raceways 92 perpendicular to the drawing plane of FIG. 3 .
  • the balls 21 which rotate at high speed throw off any chips adhering to the locking balls 21 .
  • the cooling medium adhering to the locking balls is also thrown off.
  • the locking balls are thereby kept dry and free from chips.
  • the air current circulating in the entire ring-shaped groove of the locking balls produces a strong circulating air current, which also enters the bores of the retractable nipple above.
  • the bores are labeled as sloped channel 53 and are in air communication with the adjacent horizontal channel 54 .
  • the pressure medium is guided from the air connection 44 into the upwardly sloped channel 50 , where the air exits in the region of the blow-off openings 51 .
  • a flat recess 52 is also disposed in proximity of the blow-off openings 51 .
  • the ball channel 107 through which an air current circulates, is connected via the opening 108 with the sloped channel 50 , so that both channels are connected for air transfer and the turbulence is also transferred from the ball channel 107 to the sloped channel 50 .
  • the air circulating in the ball channel 107 and in the slope to channel 50 provide superior drying efficiency for the fluid medium entering the housing of the clamping system.
  • FIG. 4 in comparison to FIG. 3 , shows a downward open center opening 55 on the clamping system.
  • the center interior space 30 in the tubular housing 1 thereby extends downwardly into the open center opening 55 .
  • the center opening 55 allows water or chips to drain or drip downwardly from the interior space 30 .
  • blow-off air which can flow through the entire inner space 30 can be introduced from the bottom via the center opening 55 (not shown in detail).
  • the retractable nipple 3 is also shown as being connected to a catch screw 56 , which under certain installation conditions causes the retractable nipple insert to be caught by a catch device and to retract into the clamping system.
  • This built-in module is characterized in that the ball support 5 forms a connected part with the spring support 6 and that the springs 7 are securely clamped between the two parts 5 , 6 .
  • the aforedescribed parts 5 , 6 , 7 are hereby combined in form of a built-in module 57 .
  • the built-in module can be easily exchanged.
  • FIG. 5 shows the second embodiment of a built-in module 58 , wherein the ball support 5 is connected with the spring support 6 by a corresponding thread 60 , with a corresponding seal 61 arranged in the gap.
  • FIG. 6 shows another embodiment of the built-in module 59 , wherein the ball support 5 is connected with the spring support 6 by a screw 64 .
  • the two parts are connected for easy disengagement.
  • Vertical blow-off bores 66 are provided in the region of the spring support 6 .
  • the ball support 5 forms an upper, approximately cup-shaped opening 63
  • the ball support 5 in the built-in module of FIG. 5 forms an approximately funnel-shaped conical opening 62 , in which the likewise conical section of the retractable nipple 3 can be inserted in a self centering manner.
  • the screw 64 is screwed into the corresponding receptacle in the ball support 5 with a seal 65 .
  • the built-in modules 57 - 59 can advantageously be easily exchanged because the position of the springs is fixed.
  • the quick-action clamping system can therefore be mounted in a vertical as well as in an overhead position without the risk that the springs move from their installed position in the built-in module.
  • FIG. 7 shows a quick-action clamping system configured as a built-in module 70 .
  • This quick-action clamping system can advantageously be inserted into an opening in a machine table or clamping plate as a module and operates completely independently.
  • the built-in module 70 is installed with screws 67 which secure the built-in module in the opening (not shown) of the machine table.
  • the employed piston 4 only needs be inserted in the cover 2 , and the completely pre-assembled built-in module 57 - 59 with the locking balls 21 placed on top can be inserted in the cover from below. This completes the installation of the entire system.
  • the retractable nipple is also shown as being connected to a workpiece palette 68 , 68 ′.
  • Clamping tools for holding the workpieces to be machined can be arranged on the workpiece palette 68 , 68 ′; alternatively, the workpieces can be attached directly to the workpiece palette 68 .
  • FIG. 8 depicts a clamping system of FIG. 7 , where the workpiece palette 68 , 68 ′ has been removed. As can be seen, the locking balls 21 protrude into the center opening 32 of the housing with a large insertion depth, which also shows the excellent support on the retractable nipple 3 .
  • Radially outer sloped bores 71 originate from the sloped channel 50 for keeping the gap of the screws 67 unobstructed.
  • the screw 64 arranged at the bottom in the housing can also be seen through the central opening 32 .
  • the sloped bores 50 are in air communication with sloped bores 69 , as shown in FIG. 7 .
  • FIGS. 9 and 10 show further details of the embodiment of a quick-action clamping cylinder according to FIG. 3 .
  • the retractable nipple 3 is connected with the workpiece palette 68 , wherein the two different semi-cross-sections illustrate again the locked and unlocked positions.
  • FIG. 10 show the position of the opposing connections, namely the pressure connections 11 in relation to the air connection 44 .
  • FIG. 11 shows another embodiment of a quick-action clamping system in the form of a built-in module 80 which is inserted as a built-in cartridge in a machine table. Importantly, the entire built-in module 80 is inserted in this central receptacle 73 in the machine table 72 , which does not require high-precision machining. The built-in module 80 is attached with screws 15 .
  • the lower spring support 6 is connected with a cylindrical tube 74 in one piece and made of the same material.
  • the cylindrical tube 74 can easily be inserted in the imprecisely machined receptacle 73 in the machine table, wherein the two seals 77 , 77 a completely seal the cylindrical tube 74 in the receptacle 73 .
  • the two seals 77 , 77 a are axially spaced apart and separate the pressure oil space from the air space.
  • the pressure medium is introduced via the connection 11 and reaches the cylinder space 12 via a ring-shaped channel 75 and a connecting bore 76 , so that the piston 4 can be moved into its unlocked position against the force of springs 7 .
  • the upper seal 77 a prevents the pressure medium from exiting at the top, and the lower seals 77 prevents the pressure medium from entering the air space below.
  • the air space 78 is in air communication with the air connection 44 and terminates via a plurality of transverse and sloped bores in the associated blow-off openings.
  • the air space 78 is in air communication with the interior space of the housing via the gap 79 .
  • a number of sloped and transverse bores extend from this interior space upwardly toward the ball contact surfaces, to the blow-off openings disposed on the cover, and to other parts.
  • the air is guided into the central interior space 30 of the housing through a central vertical bore 109 in a corresponding screw 110 .
  • the air space 78 terminates in the circumferential ring-shaped channel 81 .
  • the air-conducting gap 79 through which the compressed air is supplied to the interior space of the housing, extends from the ring-shaped channel 81 .
  • This built-in module 80 has the advantage that only the inside of the cylindrical tube 74 must be precisely machined for reliably guiding the piston 4 .
  • the entire built-in module 80 can therefore be supplied as a separate part and inserted into a relatively imprecisely machined receptacle 73 in the machine table 72 . It operates reliably, because the parts machined with high precision are arranged in the interior space of the built-in module 80 .
  • the built-in module 80 can hence be easily and cost-effectively installed.
  • FIG. 12 shows another embodiment of a clamping system which operates with an ejector piston 87 .
  • the arrangement with an ejector piston 87 having the illustrated pressure oil and air pathways can be applied to any one of the aforedescribed embodiments.
  • the described embodiment is also not limited to the illustrated clamping system.
  • the ejector piston 87 is arranged below the central interior space and below the locking system and can be displaced in the vertical direction (directions of the arrow 88 ).
  • a pressure medium is supplied via a pressure connection 111 , which is supplied to the bottom-side pressure space 85 via the gravity-fed bore 84 and a radially inward connecting groove 86 .
  • the ejector piston 87 is thereby lifted in the direction of the arrow 88 .
  • the pressure medium is supplied to the corresponding pressure space 83 via the pressure connection 82 and moved to the ring-shaped projection 112 of the ejector piston 87 , driving the ejector piston 87 downward in the direction of arrow 88 .
  • the ejector piston is installed to prevent dirt from entering the center interior hole 30 of the clamping system when the retractable nipple 3 is removed.
  • the retractable nipple 3 according to FIG. 12 is pulled out of the center inner hole 32 , the ejector piston 87 moves upward in the direction of arrow 88 and seals the center inner hole 32 towards the top.
  • the ejector piston 87 can advantageously be used for inserting retractable nipples that are connected with very heavy workpiece palettes.
  • the workpiece palette with the retractable nipple disposed below is placed on the upper end face of the ejector piston 87 .
  • the ejector piston 87 is then moved downwardly in the direction of arrow 88 by supplying pressure oil, so that the retractable nipple moves gently and controllably into the center inner hole 32 , thus preventing damage to the clamping system or locking system.
  • the ejector piston 87 has the additional advantage that chips or other contamination deposited in the interior space on the front face of the ejector piston 87 can be easily removed when the ejector piston 87 is extended.
  • Any type of pressure medium can be used and supplied through the connections 82 , 111 .
  • the ejector piston 87 can also be displaced by a spring force, without using a pressure medium.
  • FIGS. 13 and 14 show two related embodiments of clamping systems having a simple construction. This results in low installation heights, because spring assemblies can be eliminated, and locking and unlocking can be accomplished by using a pressure medium.
  • the pressure connection 93 is provided as a release connection, and the pressure connection 94 as a force-amplifying connection for amplifying the closure force of the locking ball 21 .
  • the springs 95 which are uniformly distributed along the periphery generate the locking force operating on the piston 4 , which is amplified by introducing the pressure medium via the pressure connection 94 into the pressure space 96 .
  • Unlocking is accomplished by supplying a pressure medium into the pressure connection 93 , whereby the pressure medium is supplied to the upper pressure space 97 , moving the locking piston 4 downwardly.
  • the lower ball support 91 simultaneously forms the bottom part 89 and this part is connected as one-piece and made of the same material as the afore-mentioned cylindrical tube 74 . This results in a small number of parts, namely only this part 89 in combination with the piston 4 , the cover 2 , and the associated locking balls 21 .
  • the ball support 91 forms the aforedescribed ball raceways 92 .
  • the embodiment of a surface-mounted module 100 is distinguished by a different routing of the pressure medium.
  • a vertical gravity-fed bore 98 extends downwardly from the pressure connection 94 , and terminates via a radial connecting channel 99 in the pressure space 97 .
  • a horizontal bore 91 extends from the pressure connection 93 into the pressure space 96 .
  • This embodiment also has a small number of parts and a low installation height, while operating more reliably.
  • the present invention uses turned parts that are easily machined and inexpensive, and does not require complex machining of expensive tools steels, which would significantly increase the manufacturing costs.
  • a compact quick-action clamping system with a small diameter and high locking forces is described, which operates reliably and provides an absolute positive connection in the locked position. It is therefore impossible to pull the retractable nipple out by way of a backlash (of for example 2 mm) when the system is locked, which must be accepted with conventional systems.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Jigs For Machine Tools (AREA)
  • Actuator (AREA)
US10/553,712 2003-04-15 2004-04-15 Quick action clamping cylinder with a simplified structure Abandoned US20070158891A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10317350A DE10317350A1 (de) 2003-04-15 2003-04-15 Schnellspannzylinder mit vereinfachtem Aufbau
DE10317350.1 2003-04-15
PCT/EP2004/003946 WO2004091853A1 (de) 2003-04-15 2004-04-15 Schnellspannzylinder mit vereinfachtem aufbau

Related Parent Applications (1)

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PCT/EP2004/003946 A-371-Of-International WO2004091853A1 (de) 2003-04-15 2004-04-15 Schnellspannzylinder mit vereinfachtem aufbau

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US20070158891A1 true US20070158891A1 (en) 2007-07-12

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US (1) US20070158891A1 (de)
EP (1) EP1620228B1 (de)
DE (2) DE10317350A1 (de)
WO (1) WO2004091853A1 (de)

Cited By (12)

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US20070030018A1 (en) * 2005-08-04 2007-02-08 Stefan Thurmaier Docking device actuated by pressure means
US20070063404A1 (en) * 2003-04-15 2007-03-22 Emil Stark Modular, rapid-action clamping cylinder
US20070242397A1 (en) * 2004-04-19 2007-10-18 Ralf Winkler Overload Protection Device Comprising an Electric Switching Unit
US20100219574A1 (en) * 2003-04-15 2010-09-02 Andreas Maier GmbH & Co., KG Quick action clamping cylinder with a simplified structure
US20120011690A1 (en) * 2010-05-18 2012-01-19 Apple Inc. Removable fixture for manufacturing device
US20150167719A1 (en) * 2012-07-11 2015-06-18 Almerino Canuto Device for compensating offset in automatic locking systems
US20150258647A1 (en) * 2014-03-11 2015-09-17 Erowa Ag Coupling Device For A Manipulator
CN105171499A (zh) * 2015-10-31 2015-12-23 重庆机床(集团)有限责任公司 一种直驱式滚齿机工作台
CN110769989A (zh) * 2017-06-20 2020-02-07 克斯美库股份有限公司 把持装置
CN111958514A (zh) * 2020-07-10 2020-11-20 广州市昊志机电股份有限公司 一种零点定位装置
CN114920193A (zh) * 2022-05-16 2022-08-19 山东泰东环保科技股份有限公司 一种适用于化工企业液体物料的灌装设备
WO2023001605A1 (de) * 2021-07-20 2023-01-26 Modelmakerij Hengelo B.V. Rotationsformwerkzeug

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DE102005052780B4 (de) 2005-11-05 2019-05-09 Andreas Maier Gmbh & Co. Kg Schnellspann-Zylinder mit Verriegelungskontrolle
DE102008052270B4 (de) 2008-10-18 2018-11-29 Andreas Maier Gmbh & Co. Kg Schnellspannzylinder mit Anwesenheitskontrolle des Einzugsnippels
CN102825473B (zh) * 2012-08-10 2014-07-09 昆山市和博电子科技有限公司 一种六爪中心连杆定位机构
DE102012220591A1 (de) * 2012-11-12 2014-05-15 Andreas Maier Gmbh & Co. Kg Spannvorrichtung zum Einspannen eines Einzugsnippels und Verfahren zum Einspannen einer Werkstückpalette oder eines Werkstücks
CN107097257B (zh) * 2017-05-25 2023-02-28 上海松科快换自动化股份有限公司 换枪盘

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US5918870A (en) * 1996-09-09 1999-07-06 Stark; Emil Clamping device for clamping a quick-clamp cylinder on a support plate for processing machines
US20040026843A1 (en) * 2001-04-02 2004-02-12 Walter Roth Device for the detachable mounting of workpieces on machinng devices

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8585031B2 (en) * 2003-04-15 2013-11-19 Andreas Maier Gmbh & Co. Kg Quick action clamping cylinder with a simplified structure
US7425000B2 (en) * 2003-04-15 2008-09-16 Ssa System-Spann Ag Modular, rapid-action clamping cylinder
US20070063404A1 (en) * 2003-04-15 2007-03-22 Emil Stark Modular, rapid-action clamping cylinder
US20100219574A1 (en) * 2003-04-15 2010-09-02 Andreas Maier GmbH & Co., KG Quick action clamping cylinder with a simplified structure
US20070242397A1 (en) * 2004-04-19 2007-10-18 Ralf Winkler Overload Protection Device Comprising an Electric Switching Unit
US7484612B2 (en) * 2004-04-19 2009-02-03 Schunk Gmbh & Co. Kg Fabrik Fuer Spann- Und Greifwerkzeuge Overload protection device comprising an electric switching unit
US20070030018A1 (en) * 2005-08-04 2007-02-08 Stefan Thurmaier Docking device actuated by pressure means
US7382145B2 (en) * 2005-08-04 2008-06-03 Stefan Thurmaier Docking device actuated by pressure means
US20120011690A1 (en) * 2010-05-18 2012-01-19 Apple Inc. Removable fixture for manufacturing device
US20150167719A1 (en) * 2012-07-11 2015-06-18 Almerino Canuto Device for compensating offset in automatic locking systems
US9863456B2 (en) * 2012-07-11 2018-01-09 Almerino Canuto Device for compensating offset in automatic locking systems
US20150258647A1 (en) * 2014-03-11 2015-09-17 Erowa Ag Coupling Device For A Manipulator
US9937595B2 (en) * 2014-03-11 2018-04-10 Erowa Ag Coupling device for a manipulator
CN105171499A (zh) * 2015-10-31 2015-12-23 重庆机床(集团)有限责任公司 一种直驱式滚齿机工作台
CN110769989A (zh) * 2017-06-20 2020-02-07 克斯美库股份有限公司 把持装置
CN111958514A (zh) * 2020-07-10 2020-11-20 广州市昊志机电股份有限公司 一种零点定位装置
WO2023001605A1 (de) * 2021-07-20 2023-01-26 Modelmakerij Hengelo B.V. Rotationsformwerkzeug
CN114920193A (zh) * 2022-05-16 2022-08-19 山东泰东环保科技股份有限公司 一种适用于化工企业液体物料的灌装设备

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Publication number Publication date
WO2004091853B1 (de) 2005-02-03
EP1620228A1 (de) 2006-02-01
WO2004091853A1 (de) 2004-10-28
EP1620228B1 (de) 2007-01-17
DE10317350A1 (de) 2004-11-04
DE502004002683D1 (de) 2007-03-08

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